Hydraulic transmission



Dec. 7, 1937. w, EERRlS ET AL 2,101,495

HYDRAULIC TRANSMISSION Filed Oct. 25, 1935 5 Sheets-Sheet 1 HYD' mom? ComPREssoR INYENTEIRS W AL ER Fear-us JAMES K. DOUGLAS GEmRBEfl H. 'F UBIAN ATTDRNEY.

Dec.7,1937. WQFERRISETAL 2,101,495 I HYDfiAuLic TRANSMI [S SiON Filed Oct 2:5, 1935 SSheets-Sheet 2 COMPRESSQR MP 10 H M INVEN'TURS VVALTEHFERRIS. JAMES KDEIUBLAS gamma H. FUBIAN WM ATTORNEY-I D- 1 S w. FERRIS ET AL HYDRAULIC TRANSMISSION Filed 001;. 23, 1955 3 she ts-sheets INA/ENTERS WALTER FERRls JAMEs KflDmusLAs GEDRBE H. F DBIAN WM AT 'FiDRNEY.

Patented Dec. 7, 1937- 1 UNITED STATES HYDRAULIC TRANSMISSION Walter Ferris and James K. Douglas, Milwaukee,

and George H. Fabian, West Allis, Wis., assignors to The Oilgear Company, Milwaukee, Wis a corporation of Wisconsin Application October as, 1935, Serial no. 46,328

2': Claims.

This invention relates to a hydraulic transmission which is driven from a turnable part of a vehicle, such as the axle of a refrigerator caiuand which is employed to operate. apparatus for con-5':

5 trolling the temperature within the yehlcle. such as the hydraulic transmission disclosed in appii- I cation Serial No. 673,018 filed May 26, 193301 be cooled by mechanical refrigerating apparatus and heated by circulating heated oil through a heating coil. A variable displacement pump supplies oil either as a heating agent to the heating coil or as motive liquid to a rotary hydraulic motor which drives the compressor of the refrigerating apparatus. The delivery of oil to the hydraulic motor and to the heating coil is controlled by electromagnetically operated valves under the control of thermostatically operated electric switches. The electric current for energizing the clectromagnets which operate those valves is supplied from a storage battery which is kept charged by a small generator.

The pump is driven from the car axle so the.

its speed and volumetric delivery vary in accordance with variations in car speed. In order that the compressor of the refrigerating apparatus may reach its rated speed at a low car speed and not exceed its rated speed at high'car speeds, the pump has its displacement varying element urged 'toward full stroke position by springs and urged in the opposite direction by a hydraulic servomotor which is actuated in response to variations in the velocity of the liquid flowing in the circuit. Consequently, when the car is stationary, the

pump stroke is maximum.

If the car should remain stationary for a considerable period of time in subzero weather with the pump at full stroke, the oil in the-pump. would become so thick and stiif that, when thecar was moved, the belts which drive the pump. from car axle would slip.

The present invention has as an object {to provide an improved transmission of the character described. 4

companying drawings in which the views the Another object is to provide a transmissio n'of f the above character which may be readilystarted regardless of temperature. I v

Another object is to provide means which are operable whenever-the transmission is in operation 'for supplying electric current to operate the electric controls. without the aid of a storage battery. 1

Other objects and advantages will appear from the description hereinafter given of a hydraulic transmission in whichthe' invention is embodied.

According to the invention in a general aspect and as ordinarily embodied in practice, the variable displacement pump is driven from the car axle and delivers 011 either to a heating coil or to a hydraulic motor which drives the compressor of the refrigerating apparatus. The pump has its stroke-changing element urged toward zero stroke position by a spring and toward full stroke position by a hydraulic servo-motor which is operated by liquid supplied by an auxiliary pump, and the servo-motor is actuated in response to variations in the velocity of the liquid delivered. by the variable displacement pump.

According to the invention in another aspect, electric fans which circulate air over or through the heating and cooling units and the electromagnets which operate the valves are energized by electric current supplied thereto by a generator driven by anauxiliary hydraulic motor which is connected in series with the main hy- .draullc motor, and the speed of the auxiliary motor is limited by by-passing all liquid in excess of the liquid. required to drive the auxiliary motor at a predetermined speed through a speed controller which operates in response to, variations in the velocity of the liquid flowing in the circuit.

The invention is exemplified by the hydraulic transmission shown schematically in the acfollows:

. Fig. 1 is a diagram of the hydraulic circuit and shows the several parts thereof in the positions occupied when the transmission is idle.

Fig. 2 is a similar diagram showing the several parts of the transmission in the positions occupied when the main hydraulic motor is driving the compressor of the refrigerating apparatus and the displacement of the pump is being increased.

Fig. 31s a similar diagram showing the several :parts of the transmission in the positions occupied when the pump is supplying liquid to the heating coils and the displacement of the pump is being maintained substantially constant.

The transmission is shown as being employed are as -invention. If the car needs to be cooled, the compresso to supply oil as a heating agent to the heating coils and to operate the refrigerating apparatus of a refrigerator car of which only a heating coil I and the compressor 2 of the refrigerating apparatus are shown for the reason that the heating and cooling apparatus form no part of the present is driven by a rotary hydraulic motor 8 when the car is in transit and by an electric motor 4 when 'the car is stationary. Current for operating the V electric motor 4 may be supplied thereto from'a" stationary electric circuit through twoconductors 5 and 8 which are connected to the motor-4 andprovided at the outer ends thereof with a con .nector 1 for connection to the stationary electric Liquid for driving the hydraulic motor a is.

supplied by a variable displacement pump ll which is driven from the axle of the car so that the pump is idle when the car is stationary and is driven in one direction or the other when the car is in transit, depending upon the direction of car movement.

In order to clearlyillustrate the hydraulic circuit, the several parts of the transmission are shown separated from each other but, in practice, the pump and the motor ,3- are arranged in a single casing and the several valves which control the operation of the apparatus are arranged in a casing mounted upon the pump and motor casing as shown in the application referred-to above.

' The channels which connect the several parts of the transmission consist in part of pipes and in part 01' channels formed inthe casing of the pump and motor and in the casing of the control unit. For the purpose of explanation, however, they will be referred to herein as pipes.

The pump in is provided with a displacement varying slide block Ii which is at all times urged in a direction to decrease pump displacement by two springs l2 and which, when the pumpis in operation, is urged in a direction to increase pump displacement'by a hydraulic servo-motorthe piston ll of which is connected to the slide block H and fitted in a cylinder I4 formed in a casing I! which is ordinarily a part of the pump casing. The arrangement is such that the springs I2 can move the slide block to its zero stroke position as soon as the pump ceases to operate.

The pump III has a pipe I6 and a pipe ll connected thereto. When the car is in transit, the pump discharges liquid into one of these pipes and has liquid returned to it through the other pipe depending upon the direction of car movement and the resultant direction of pump actuation.

The pipes l6 and vI'I are connected, respec-' tively, through check valves l8 and ii to one end of a supply pipe and through check valves 2i and 22 to one end of a return pipe 23. The check valves permit liquid to flow from either the pipe It or the pipe 11 into the supply pipe 20 and from the return pipe 23 into either the pipe It or the pipe I! but prevent it from flowing in the opposite direction in order that the pump may deliver liquid into the pipe 2| and have liquid returned to it through the pipe 23 in either direction 0! pump actuation.

The supply pipe 20 has its other end connected to the casing of a selector valve 24 in communication with an annular port 25 formed therein between two. similar ports 20 and 21. Liquid discharged by the pump II is directed by the selector valve 24 either to the heating coil I 'or to a convalve 2!.which controls the delivery of liquid to the hydraulic motor 1.

The flow of liquid through the valve 24 is controlled by ,its plunger 20 which is urged toward the left to the position shown in Fig. 1 by a spring II and, is adapted to be moved toward the right into the position shown in Fig. 3 by liquid delivered to the left end of the valve casing through a pipe II as will presently be explained.

Theportliisconnected byapip'e I2toan annular port a formed in'the casing of the con-- trol valve 20. The port 21 is to the inlet end of the heating coil I by a pipe which has a restriction such as an orifice choke 8| arranged therein to cause thccncrgy in the oil forced therethrough to be transformed into heat to heat the oil. The discharge end of the coil I is connected by apipe 3' to the casing of the control valve 28 at a point between the port Cl and a port 81.

When the plunger 2| 0! the selector valve 24 is ifi the position shown in Fig. 1, liquid discharged by the pump ll flows through the valve casing to the control valve 28. When the plunger 2' is in the position shown in Fig. 3, liquid discharged by the pump lll flows through the valve casing and the pipe 84 to the heating coil 1.

The flow of liquid through the control valve 22 is controlled by its plunger 28 which is urged toward the left to the position shown in Fig. l

by a spring 38 and is adapted to be moved toward the right into the position shown in Fig. 2 by liquid supplied to the left end of the valve casingthrough a pipe 40 as will presently be explained.

The port 33 of the control valve 28 is connected to the inlet of the hydraulic motor I by a pipe 4|.

The port 31 is connected by a pipe 42 to a pipe 42- intermediate the ends thereof. The pipe ll is thus inconstant communication with the pipe 40 through the pipe 42 irrespective of the position of the valve plunger 30.

The pipe 48 has one of its ends connected. to the outlet port of thevmotor l and its other end connected to the inlet port of an auxiliary hydraulic motor 44 which drives an electric generator 45 and discharges into a pipe 46.

The motor 44 is thus connected in series with the motor I but it is smaller so that it would run -faster if the entire discharge from the motor I 'in' parallel to the passage 62 and encircled intermediate its ends by an annular port 54 which is connected by a pipe to the pipe 43 intermediate the ends thereof.

The valve bore 53 communicates at one of its ends with a cylinder 56 and at its other end with an unrestricted passage 58 and thereby provides portion provides a seal between the port 54 and the counterbore 51 when the valve is shifted at a sumcient distance toward the left.

Intermediate its end portions, the valve 59 is provided with suitable grooves which are, lon

:enough to permit liquid to flow from the port- 54 to the counterbore 51 and which are shaped to throttle the flow.

The valve-"59 is urged toward the right to open -communication between the port 54 and the counterbore 51 by a piston 55,.which is closely fitted in the'cylinder 55, and it is urged toward the left to close communication between the port '54 and the counterbore 51 by a helical compression spring 5! arranged in the counterbore 5'l between the end of the valve and the end of an adjusting screw threaded through the end of the casing. l

The piston 55 is actuated in response to varia tions in the drop in pressure across an orifice choke 52 which is arranged in the discharge passage 52 near the inlet end thereof and provided with an orifice through which theentire the piston 55 through two passages which are ordinarily restricted to prevent the valve 59 from hunting and which are arranged upon opposite sides of the choke 52 and communicate with opposite ends of the cylinder 55, r

When the transmission stops, the spring 5| moves the valve 59 toward the left and closes the port 54 to the counterbore 51 as shown in Fig. 1. Then, when the transmission is started,

. the entire volume of liquid flowing in the pipe 43 is at first directed to the auxiliary motor 44 and tends to drive it at a speed proportional to the rate of flow in the pipe 43.

As the motor 44 attains speed, the flow through the passage 52 increases and causes a drop in pressure across the choke 52. The pressure prevailing at the left of the choke 52 will extend into the left end of the cylinder 55 and exert a force upon the left end of the piston 59, and the pressure prevailing at the right of the choke 52 will extend into the right end of the cylinder 55 and exert a force against the right end of .the piston 50. The pressure prevailing at the right of the choke 52 will also extend through the passage 58 into the counterbore 51 so that both ends of the valve 59 are subjected to the same pressure.

As the motor speed continues to increase, the velocity of the liquid discharged therefrom will continue to increase and cause the drop in pressure across the choke 52 to increase until the I force exerted against the piston by the liquid at the left. of the choke 52 becomes great enough to move the piston and the valve 59 toward ;the right against the forces exerted against the right end of the piston 55 by the spring 5| andby the pressure prevailing at the right of the choke 52.

Shifting the valve 59 toward the right opens the port 54 to the counterbore 51-, as shown in Fig. 2, thereby permitting liquid to flow from pipe 43 through'the pipe 55, the port 54, the

counterbore 51 and the passages 55 and 52 to the return pipe 23 at a rate determined by the.

- distance the valve 59 is opened. The valve 59 throttles the flow therethrough in order to limit it and to maintain adequate pressure in the pipe 43. v

The hydraulic force exerted upon the left end of the piston 55 in excess of the hydraulic force exerted on the right end thereof opposes the forceoi the spring 5! and causes the valve "to float in abalanced condition between these two forces.

all liquid in excess of the liquid required to drive the motor 44 at a predetermined speed which is determined jointly by the area of the orifice in the choke 52 and the resistance of the spring 5|.

A change in the rate at which liquid flows through the pipe 43 or a change in the load on the motor 44 will cause a momentary change in the rate of flow through the motor'44 and consequently through the choke 52. This change in flow initiates almost instantly a readjustment of the valve 59 to such a position that the rate' at which liquid is by-passedis varied in proportion to the change in flow, thereby causing the motor to continue to operate at substantially the predetermined speed.

In order to limit the pressure of the liquid delivered to the auxiliary motor 44 when liquid is being supplied thereto by the main motor 3, which at this time-is driven by the electric motor 4 and is functioning as a pump, a relief valve 53 is provided. As shown, the relief valve 53 has its inlet connected to the pipe 55 and its outlet connected to the counterbore 51.

Liquid for operating the controls and for supercharging the pump in when the car is in transit is provided by a gear pump 55 which is driven in unison with the pump '10 and is ordinarily arranged in the casing therewith as substantially a part thereof according 'to the usual practice.

Liquid for operating the controls and for supercharging the motor 3 is provided by a gear pump 51 when the car is stationary and the motor 3 is being driven by the electric motor 4 and is functioning as a pump. The gear pump 51 is driven in unison with the motor 3 and is ordinarily arranged in the casing therewith-as substantially a part thereof, the motor 3 ordinarily being substantially the same as the pump H] except-that it is not adjustable to vary its displacement.

The gear pumps 55 and 51 draw liquid from a In this position, the valve 59- by-passes' therefore delivers liquid in one direction or'the peripheral surface intermediate its ends with a other depending upon the direction of car movement, it is necessary to provide for directing its 'output into the pipe 88 in either direction of pump actuation.

As shown, the gear pump 81 draws liquid from the reservoir 58 through a suction pipe 1| and discharges it into a pipe 12 which is connected through a check valve 13 to the low pressure supply pipe 88 and through a check valve 14 to a pipe 15 through which the gear pump 88 draws liquid from the reservoir 58. The gear pump 88 has one of its ports connected to the pipe 12 and its other port connected to a pipe 18 which is connected to the pipe 58 through a check valve 11 and to the pipe 15 through a check valve 18.

The gear pump 86 will draw liquid from the reservoir 58 through the pipe 15, check valve 18 and pipe 18 and discharge it through the pipe 12 and check valve 13 into the pipe 68 in one direction of pump actuation, and it will draw liquid from the reservoir 88 through the pipe 15, check valve 14 and pipe 12 and discharge it through the pipe 16 and check valve 11 into the pipe 88 in the other direction of pump actuation.

One function of the pump 88 is tosupply liquid for operating the servo-motor I3-|4 to change the displacement of the pump I8. The flow of liquid to and from the servo-motor is controlled by a valve 18 which is operated in response to variations in the rate at which the pump I8 forces liquid through the hydraulic circuit as reflected by the drop in pressureacross an orifice choke 88 which for convenience is ordinarily arranged in the passage 52 of the motor speed controller 58 between the entrance to the passage 58 and the entrance to the return pipe 23.

The valve 18 has an axial bore 8| formed in its casing and three ports 82, 83 and 84 formed in the wall of this bore. The port 82 is connected by a pipe 85 to the return pipe 23 intermediate the ends thereof, the port 84 is connected by a pipe 88 to the head end of the cylinder I4, and the port 83 is connected by a pipe 81 to a drain pipe 88 which discharges into the reservoir 68. The pipes 86 and 81 have chokes 88 and 88 connected therein, respectively, to restrict the flow of liquid to and from the cylinder I4 to therebyprevent the stroke of the pump from being changed too suddenly.

The flow of liquid through the valve 18 is controlled by a valve member or plunger 8| which is closely fitted in the bore 8| and provided in its plurality of longitudinal grooves 82 through which liquid may flow from the port 84 to the port 88 when the plunger 8| is urged toward the left as shown in Fig. 1. Suitable grooves are also formed in the peripheral surface of the valve plunger 8| at the left end thereof to limit the flow of liquid fromthe left end of the bore 8| to the port 84.

Th valve plunger 8| has an axial duct 88 extending inward from theleft end thereof into communication with a plurality of radial ducts 84 which communicate with the port 82 in any position of the valve plunger. The duct 83 has a choke 85 arranged therein to limit the rate of flow therethrough to thereby prevent the piston I3 and slide block II from hunting.

The left end of the plunger 8| is thus exposed to the pressure prevailing in the return pipe 28. This pressure urges the plunger 8| toward the is by-passed around the choke 88.

right with a force which is constant and proportional to the resistance of the gear pump relief valve 18. The valve plunger 8| is also urged toward the right by a light spring 88 arranged in the left end of the bore 8| and reacting against a plug which closes. the,end of the bore 8| and serves as a stop to limit the distance the valve plunger 8| may move toward the left.

The bore 8| is open at its right end to a counterbore 81 which is considerably greater in crosssectional area and has a hollow piston 88 fitted therein. The piston 88 is urged toward the left by a helical compression spring 88 which is arranged inside the piston 88 and reacts against a plug I88 which closes the right end of the counterbore 81.

In order that the piston 88 may not have its movement hampered by liquid or gas trapped in the counterbore 81, it has a plurality of openings 8| formed in its side wall and communicating at all times with an annular port I82 which is formed in the wall of the counterbore and connected by a pipe I88 to the drain pipe 88.

The left end of the counterbore 81 is connected by a pipe I 84 to the passage 52 at a point between the chokes 82 and 88 so that the piston 88 and the end of the plunger 8| are subjected to the pressure prevailing therein. This pressure is great enough to hold the piston 88 in retracted position. The pipe I 84 has connected therein a check valve I85 which permits liquid to flow from the passage 52 to the counterbore 81 but prevents it from flowing in the opposite direction.

In order that liquid may escape from between the plunger 8| and the piston 88 when the plunger moves toward the right, one or more small rooves I88 are formed in the surface of the plunger 8| andextend longitudinally thereof far enough to provide communication between the port 82 and the counterbore 81. When the plunger 8| moves toward the right, liquid is ejected from between it and the piston 81 through the grooves I86 and the port 82 into the pipe 85.

If it were notfor the grooves I88, the entire volume of liquid discharged by the pump I8 would flow through the choke 88. As it is, there is a constant limited flow through the grooves I88 from the pipe I84 to the pipe 85 so that this flow Therefore, the area of the orifice in the choke 88 must be determined in view of the flow through the grooves I88. However, the flow through the grooves I88 is so small that it has no appreciable effect upon the operation of the apparatus and, hence, it will be disregarded in the explanation hereinafter given.

Since the left end of the plunger 8| is exposed to the pressure prevailing in the return pipe 28 and since the right end of the plunger 8| is exposed to the pressure prevailing in the passage 52, the plunger 8| is urged toward the left against the resistance of the spring 86 by a force which is proportional to the difference between the pressures prevailing upon opposite sides of the choke 88. The spring 85 has its tension adjusted to counterbalance this force and hold the plunger 8| in position to substantially-close the port 84 when the motor 8 is opetatinglat the desired speed. That is, the plunger 8| floats in a balanced condition between the two forces. The

ent size orifice.

Variation in the speed of the car will cause a variation in the speed of the pump l and a resultant momentary variation in the rate of pump delivery. A variation in the rate of pump delivery will cause a variation in the velocity of the liquid flowing in the circuit and a variation in the speed of the motor 3. A variation in the velocity of the liquid will cause a variation in the drop in pressure across the choke 80.

When the car speed increases with the resultant increasein the velocity of the liquid, the pressure in the pipe I04 will increase and move the plunger 9! toward the left and thereby open the port 84 to the port 83 so that the springs I2 may move the slide block Ii toward the right to decrease pump displacement and the piston l3 may eject liquid from the cylinder I4 through the pipe 86, the ports 84 and 83, and the-pipe 81 into the drain pipe 88.

The displacement of the pump I0 will be reduced until the motor 3 is operating at the de sired speed at which time the pressure in the pipe E04 will have dropped suficientlyto permit the spring 93 to move the plunger 9i toward the right to close the port 84 to the port 83, thereby trapping liquid in the cylinder id to maintain the adjustment of the pump l0.

When the car speed decreases with the resultant decrease in the velocity of the liquid, the pressure in the pipe I04 will decrease and permit the spring 96 to move the plunger 9| toward the right and thereby open the port 84 to the left end of the bore 8| so that liquid may flow from the pipe 23 through the pipe 85, the ducts 94 and 93 to the left end of the bore 8I and then through the port 84 and the pipe 86 to the right end of the cylinder I4 and move the piston 53 and the slide block I! toward the left to increase the displacement of the pump and thereby increase pump delivery.

The displacement of the pump it will be increased until the motor 3 is operating at the elesired speed, at which time thepressure in the pipe E04 will have increased sufficiently to overcome the resistance of the spring 96 and move the plunger 9| toward the left to close the port 84,

thereby trapping liquid in the cylinder I4 to maintain the adjustment of the pump 60.

In order to prevent the pump l0 from becoming overloaded, it is provided with a relief valve I I0 which is shown as having its inlet connected to the supply pipe 20 by a pipe H l and its outlet connected to the pipe M4 by a pipe M2.

Since the same torque applied to the pump will enable it to create a higher pressure at a short stroke than at a longer stroke, provision is ordinarily made for varying the resistance of the relief valve H0 in accordance with variations in pump displacement.

As shown, the relief valve M9 is arranged in the servo-motor casing E5 in alinement with the cylinder I4, and the spring N3 of the relief valve reacts against a stem H4 which is movable with the piston i3 and is closely fitted in the casing l5 to prevent the escape of liquid from the cylin der I4.

When the slide block I I moves toward the right to decrease pump displacement, the stem M4 compresses the spring H3 and thereby increases the resistance thereof. When the slide block it moves toward the left to increase pump displacement, the stem H4 permits the spring M3 to expand and thereby decreases the resistance there- The arrangement is such that the relief valve H0 will open only at a high pressure, for instance 2000# per sq. in., when the pump is operating at a minimum stroke but it will open at a lower pressure, for instance 900# per sq. in., when the pump is operating at maximum stroke.

If the pressure should exceed the maximum determined by the resistance of the spring II3, the relief valve IIO would open and permit liquid from the pipe III to' flow therethrough and through pipes H2 and I04 to the valve "I9 and move the plunger 9| thereof toward the left and thereby permit the springs I2 to reduce pump displacement as previously explained.

Operation of the selector valve 24 is controlled by a. pilot valve I20 having three ports I2I, I22 and I23 formed in its casing and controlled by a valve member or plunger I24 which is urged toward the left to the position shown in Fig. 1 by a spring I25 and is adapted to be moved toward the right to the position shown in Fig. 3 by a solenoid I26 to which-it is connected.

In order that movements of the plungers 29 and I24 of the selector and pilot valves may not be hampered by entrapped liquid or gas, the right end of the selector valve casing and both ends of the pilot valve casing are connected to branches of the drain pipe 88.

The port I2 I is connected to another branch of the drain pipe 88, the port I22 is connected to the pipe 3I through which liquid is'delivered to the selector valve for operating it, and the port I23 is connected to one branch of a. pipe i2? which is connected to the pipe 36 intermediate the ends thereof.

Whenever the transmission is in operation, the resistance of the auxiliary motor 44 causes pressure to be created inthe pipe 43. This-pressure extends through the pipe 42, the casing of the control valve 28, and pipe 36 to the pipe I21 so that, when the pilot valve plunger I24 is shifted toward the right to the position shown in Fig. 3, liquid may flow from the pipe I21 through the pilot valve l2!) and the pipe 3| to the selector valve 24 and shift its plunger 29 toward the right to the position shown in Fig. 3.

When the pilot valve plunger I24 is returned to the position shown in Fig. 1, port I22 is opened to 'port HI and the spring 30 may move the plunger 29 toward the left and cause it to eject the right to the position shown in Fig. 2 by a soleniod E36 to which it is connected.

In order that movement of the plungers 38 and 134 of the control and pilot valves may not be hampered by entrapped liquid or gas, the right end of the control valve'casing and both ends of the pilot valve casing are connected to branches of a drain pipe I31 which is connected to the drain pipe 83 intermediate the ends thereof.

The port 538 is connected to another branch I of the drain pipe I31, the port I32 is connected to the pipe 40 through which liquid'is delivered to the control valve for operating it, and the port 1133 is connected to the other branch of the pipe 02?.

When the pilot valve plunger I34 is in the position shown in Fig. 2, liquid may flow from -matter carried by the oil.

the pipe I2I through the pilot valve I66 and the pipe 46 to the control valve 26 and shift its plunger 66 toward the right to the position shown in Fig. 2.

When the pilot valve plunger I64 is moved to the position shown in Fig. 3, port I62 is opened to the port III and the spring 66 may move the plunger 66 toward the left and cause it to eject liquid from the left end of the control valve casing through the pipe 46 and the pilot valve I36 into the drain pipe I61.

In order that the plungers of the valves 24, 26, I 26 and I36 may not operate too rapidly, suitable chokes are provided. If a single orifice choke should be employed to limit the rate of movement of each plunger, the orifice therein would be so small that it would become clogged by foreign As shown, the movement of each plunger in each direction is limited by two chokes arranged in series. 3

The solenoids I26 and I66 are operated by electric current supplied thereto by the generator 45 under the control, respectively, of electric switches I46 and I which are operated, re-

spectively, by thermostats I42 and I46 arranged within the interior, of the refrigerator car.

The switch I46 has one of its terminals connected to one terminal of the generator 46 by'a conductor I44 and its other terminal connected by a conductor I46 to one end of the winding of the solenoid I26 the other end of which is connected to the other terminal of the generator 46 by a conductor I46. The switch I has one of its terminals'connected to the conductor I44 and its other terminal connected by a conductor I41 to one end of the winding of the solenoid I66 the other endof which connected to the conductor I46. 1

The thermostats I42 and I46 respond to variations in the temperature within the refrigerator car and open and close the switches I46 and I to direct liquid to the heating coil I, or to the hydraulic motor 6, or to neither.

The generator 46 also supplies current for driving a plurality of electric fans I46 which circulate air over or through the heating and cooling units when the tra is in operation. Since the present invention resides in the drive for the air conditioning apparatus and not in that apparatus per se. only on'e of the fans I46 has been shown. This fan is shown connected to the conductors I44 and- I46, respectively, by conductors I46 and I66.

Operation Assuming that the car is stationary and that the temperature therein is too high, the several parts of the transmission will be in the positions .shown in Fig. 1.

- When motion is imparted to the car, the pumps I6 and 66 will be driven from the car axle. The ear pump 66 will immediately deliver 011 into the pipe 66, thereby creating pressure therein, but the pump I6 will not deliver any oil at first for the reason that it is at zero stroke.

The oil delivered by the gear pump 66 into the pipe 66 will flow therethrough and through the pipe 23, passage 62, check valve I66 and pipe I64 to the left end of the counterbore 61 and act upon the adjacent ends of the piston 66 and the valve plunger 6|, and it will move the piston 66 toward the right to the position shown in Fig. 2 for the reason that the cross-sectional area of the piston 66 is great enough to enable the gear pump pressure to overcome the resistance of the spring 66.

The pressure created by the gear pump 66 will extend through the pipes 26 and 66 and the bore II as shown in Fig. 2.

Oil delivered by the gear pump into the pipe 66 may then flow through the pipes 26 and 66, the valve I6 and the pipe 66 to the cylinder I4 and move the piston I6 and the slide block II toward the left and thereby cause the pump I6 to deliver oil into either the pipe I6 or the pipe I'I depending upon the direction of car movement.

When the pump I6 starts to deliver oil into the supply pipe 26, the motor 6 will not be started immediately due to the fact that it is by-passed by the plunger 66, of the control valve 26 being in the position shown in Fig. 1, but liquid may .flow from pipe" 26 through valve 24, pipe 62,,

valve 26 and pipes 42 and 46 to the auxiliary motor 44 to start it. 1

The resistance of the motor 44 will cause liquid to flow from the valve 26 through pipes 66 and I21, pilot valve I66 and pipe 46 to the left end'of the casing of valve 26 and move its plunger 66 toward the right to the position shown in Fig. 2, thereby connecting the motor 6 in series withthepump I6. 1

Due to the throttling eifect of the chokes 66 and 66 and the groov'es in the left end of the plunger 6i, the slide block II will move slowly. Consequently-when the pump 16 starts to deliver oil into the pipe 26, it is at short stroke and is therefore able to create a high pressure to overcome the static inertia and friction of the motors 6 and 44 and the mechanisms driven thereby.

Since the car is at first moving at slow speed, so that the pump I6 is being driven at slow speed, the slideblock II will continue to move toward the left until the pump I6 is at full stroke. I

The oil discharged by the pump II will flow through the pipe 26, the selector valve 24 via the ports 26 and 26, the pipe 62, the control valve 26 via the port 66, the pipe 4|, the motor 6, the pipe 46, theauxiliary motor 44, the pipe 46, the passage 62, the return pipe 26 and the pipe II or I6 back to the pump I6.

As the car speed increases with the resultant increase in pump speed, the volumetric delivery of the pump I6 will be increased and thereby increase the speed of the motors 6 and 44. The entire output of the pump I6 will flow through the auxiliary motor 44 until that motoris drivingthe generator 46 at its rated speed and then the drop in pressure across the orifice choke 62 will be suillcient to operate the speed controller 66 which will then bypass all of the oil delivered by the pump I6 in excess of that required to drive the auxiliary motor 44 at the desired speed as previously explained.

As the car speed continues to increase with the resulting increase in pump delivery, the speed of the motor 6 will continue to increase until it is driving the compressor 2 at its rated speed. In practice, the compressor 2 attains its rated speed at a low car speed, for instance 18 miles per hour, and the auxiliary motor 44 is so proshown in Fig. 3, where it covers the port 84 and floats in a balanced condition. A further increase in car speed will cause this pressure differential to increase and move the valve plunger 9! toward the left to open the port 84 to the port 83 and thereby permit the springs [2 to.

decrease pump displacement in proportion to the increase in car speed. The port 84 will remain open to the port 83 and the springs l2 will con- I tinue to decrease pump displacement as long as the car speed continues to increase.

When the car speed becomes constant, the pressure differential across the orifice choke 80 will become equal to the resistance of the spring as which will move the valve plunger 9| far enough to cover the port 8 3, as shown in Fig. 3, where it will float in a balanced condition as pre viously explained. Thereafter, any variation in car speed will cause the valve plunger 8i to move in one direction or the other to cause the pump displacement to be varied in proportion to vari ations in car speed and thereby maintain the motor speed constant as previously explained.- It is to be understood that the valve plunger 95 does not ordinarily'move very far from its centill tral position except when the pump it is idle, the movement of the plunger Q! having been exaggerated in the drawings for clearness of illustration. The motor 3 will continue to drive the com pressor 2 until the temperature within the car has been reduced to a predetermined degreeior instance 35 F., and then the thermostat M3 will close the switch lfil to enable the generator 35 to energize the solenoid i36 which will shift the plunger i3 3 of the pilot valve I toward the right to the position shown-in Fig. 3, thereby opening port Hi to port E32 and permitting spring 38 to shift the valve plunger 38 toward the left to the position shown in Fig. 3.

Shifting the valve plunger 38 to the position shown in Fig. 3 opens the port it? to the port and thereby bypasses the motor 3 which ceases to drive the compressor 2. The oil will then flow from the pipe 32 through the control valve 2%? and the pipe d2 into the pipe 93, thereby causing the auxiliary motor ifi to continue to operate as formerly. I

The valve 28 will continue to bypass the motor 3 until the temperature in the car exceeds a predetermined degree, for instance 37 F., at which time the thermostat i 33 will open the switch Ml to deenergize the solenoid I38 and thereby permit the spring wt to shift the valve plunger i3t toward the left to close the port iii and open the port l33. Then oil will flow through the pilot valve and move the valve plunger 38 toward the right to close the port 33 and'thereby cause the motor 3 to be energized and drive the compressor 2 to cool the car as previously described.

If the car is subjected-to low temperatures and the temperature within the car drops to a predetermined minimum, for instance 33 F., the switch M! will be operated first by the thermostat MS to cause the motor 3 to be bypassed, and then the thermostat I42 will close the switch Mil to enable the generator 45 to energize the solenoid l26 which will shift the plunger i2 5 of the pilot valve E29 toward'the right to the position shown in Fig. 3, thereby permitting oil to flow from the aromas pipe through the pipes 62, 36 and H27, ports I23 and I22 of the pilot valve i2ll and pipe iii to the left end of the valve 23 and shift its plunger 29 toward the right into the position shown in Fig. 2.

Shifting the plunger 29 of the selector valve to the position shown in Fig. 3 closes communication between the ports 25 and 26 and opens communication between the ports 25 and 21, thereby stopping the delivery of oil into the pipe 32 and directing it through the pipe 34 into the coil I, the oil being heated as itis forced through the choke 35 to thereby provide the coil l with hot oil to heat the car. After passing through the. coil l, the oil flows through the pipe 36, valve 28 and pipe 52 into the pipe 33 so that the auxiliary motor M continues to be driven as formerly.

The pump it will continue to force its entire output through the choke 35 and coil l to heat the temperature therein during the time the car is in transit, oil will be delivered at a substantially constant rate to the motor 3 as a motive agent or to the heating coil as a heating agent when the car is moving at or above a predetermined low speed, and the generator 35 will be driven at a, substantially constant speed when the car is moving at or above a predetermined lower speed.

When the car stops and thereby ceases to drive the pumps. the pressure in the circuit will drop substantially to zero and permit the spring 99 to move the piston 93 and plunger ill of the valve 79 toward the left to the position shown in Fig. I. With the plunger 99 in this position, port 85 is open to port 83 and the springs I? may move the slide block ll toward the right to its zero displacement position and cause the piston iii to eject oil from the cylinder i i through pipe td 'valve it mission is thick and stiff due to the car remainrotates without tending to displace any of the oil and the gear pump 86 is so small that but little power is required to drive it.

The gear pump 56 will first break up the thick oil therein and impart heat thereto and then force the thick oil into the pipe 69. If the oil in the circuit is so thick that the gear pump cannot move it, the liquid discharged by the gear pump will be forced through'the relief valve i8 and the energy stored in the oil will be transformed into heat.

Since the gear pump 86 is arranged within the same casing as the pump Hi, the heat generated by the gear pump and at the relief valve 70 will heat the oil therein. Hea is also imparted to the oil by rotation of the rotor of the pump it.

When the oil has been warmed slightly, it will flow very slowly to the valve 79 and operate it the relief valve H3,

and then it will flow very slowly to the cylinder l4 and movethe piston i3 and the slide block ii slowly toward the left.

As the slide block it starts to move toward the left, the pistons of the pump III will at first discharge minute quantities of oil into the pipe l6 or the pipe I! depending upon the direction of car movement. If the oil in the remote parts of the circuit is so thick and stiff that the pump iii cannot moveit, the pump will discharge through thereby further heating the oil.

The transmission will continue to operate in this manner until suflicient heat has been genminutes after having been started with the oil so cold and still that it is semisolid.

If the car needsto be cooled while stationary and the connector I is attached to the connector 8 of a stationary electric circuit, the electric motor 4 will be energized and drive the compressor 2 to cool the car. Since the motor I is direct-connected to the compressor 2, it will be driven in unison therewith and function as a pump to supply liquid for driving the auxiliary motor 44.

The gear pump 81, which is driven in unison with the motor 3, will draw liquid from the reservoir 68 and deliver a part of it into the return side of the circuit for control purposes and to maintain a low pressure therein in order that the speed controller ill may function properly. Liquid discharged by the gear pump 81 in excess of these requirements is exhausted through the relief valve 10.

The hydraulic motor 3, when driven by the electric motor 4 and functioning as a pump, will discharge liquid into the pipe 43 and have liquid returned to it through the pipe 4i. When it starts to function as a pump, the pipe 43 is open to the pipe 4i through pipe 42 and valve 28 so that the liquid is short circuited momentarily. However, liquid discharged by the gear pump 51 immediately flows through pipe 12, check valve 13, pipes 69 and 23, check valve 2i or 22, pipe 16 or II, check valve II or l9, pipe 20, valve 24 and pipe 32 into valve 20 and creates pressure therein and in pipes 4i, 42 and 43. From valve 28, liquid flows through pipes 36 and I21, pilot valve I30 and pipe 40 to the left end of valve 28 and moves the plunger 38 towards the right to .close communication between pipes 4i and 42,

thereby directing liquid from the-motor 3 to the auxiliary motor 44 to cause it to drive the generator 45 which will then supply an electric current for operating the fans I48.

From the motor 44, the liquid will flow through the pipe 48 and passage 52 into the return pipe 23, and all liquid discharged by the motor 3 in excess of that required to drive the motor 44 at the desired speed will be bypassed through the pipe 55 and the speed controller "into the return pipe 23 in the manner previously described. From the return pipe 23, the liquid will flow through pipe I or- II, supply pipe 20, valve 24, pipe 32, valve 28, and pipe 4i back to the motor 3.

It will be moted that the pressure created by the motor) extends through pipes 42, I6 and I21,

coil i and pipe 34 but there will be no flow therethrough due to thepipe 34 being blocked by the plunger 29 and the pipe I21 having one end blocked by plunger I24 and its other end open only to the left end of valve 20 the plunger I! of which has previously been moved toward the right to the limit of its movement.

The electric motor 4 will continue to drive the compressor 2 as long as it is connected into the stationary electric circuit. After the car has been cooled to the desired degree, the refrigerant will be diverted from the car cooling coils to the coils in the brine tanks through which it my flow for a long period of time, thereby permitting the attendant to disconnect the motor 4 from the stationary circuit at his convenience.

The invention herein set forth is susceptible of various modifications and adaptations without departing from the scope thereof as hereafter claimed.

The invention is hereby claimed as follows:

1. The combination with an enclosed space,

and air conditioning apparatus to cool said space,

of a hydraulic motor for driving said apparatus,

a radiator arranged within said space to cause liquid forced therethrough to heat said space. a

pump, means for directing liquid from said pump to said motor and to said radiator selectively, and means for driving said pump.

2. The combination, with a vehicle, and air conditioning apparatus to cool the interior of said vehicle, of a hydraulic motor for driving said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, and means for directing liquid from said pump to said motor and to said radiator selectively.

3. The combination, with a vehicle, and air conditioning apparatus to cool the interior of said vehicle, of a hydraulic motor for driving said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means for directing liquid from said pump to said motor and to said radiator selectively, and means for varying the displacement of said pump inversely to variations in the speed of said vehicle.

4. The combination, with a vehicle, and air conditioning apparatus to cool the. interior of said vehicle, of a hydraulic motor for driving said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means for directing liquid from said pump to said motor and to said radiator selectively, and means responsive to variations in the velocity of the liquid circulated by said pump for varying pump displacement inversely to variations in the speed of said vehicle.

5. The combination, with a wheeled vehicle. and air conditioning apparatus carried by said vehicle to cool the interior thereof, of a hydraulic motor for driving said apparatus, a radiator carried by said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump, means for directing liquid from said pump to said motor and to said radiator selectively, and a drive connecting said pump to a wheel of said vehicle to drive said pump from said wheel.

6. The combination, with a wheeled vehicle, and air conditioning apparatus carried by said vehicle to cool the interior thereof, of a hydraulic motor for driving said apparatus, a radiator carried by said vehicle to cause liquid forced there- '-through to heat the interior of said vehicle, a

pump, means for directing liquid from said pump to said motor and to said radiator selectively, a

drive connecting said pump to a wheel of said vehicle to drive said pump from said wheel, and means for varying pump displacement inversely to variations in wheel speed to thereby maintain pump delivery substantially constant within a wide range of wheel speeds.

7. The combination, with a wheeled vehicle,

and air conditioning apparatus carried by said' vehicle to cool the interior thereof, of a hydraulicmotor' for driving said apparatus, a radiator carried by said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump, means for directing liquid from said pump to said motor and to said radiator selectively, a

drive connecting said pump to a wheel of said vehicle to drive said pump from said wheel, and a motor for driving said apparatus, a radiator carried by said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump, means for directing liquid to said motor and said radiator selectively, a drive connecting said pump to a wheel of said vehicle to drive said pump from said wheel, and means for directing the output of said pump in a given direction irrespective of the direction of wheel rotation.

9. The combination, with a vehicle and air conditioning apparatus carried by said vehicle for cooling the interior thereof, of a hydraulic motor for driving said apparatus, a radiator carried by said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means for directing liquid from said pump to said motor and to said radiator selectively, an

electric motor for driving said apparatus, and means for connecting said motor into a stationary electric circuit when said vehicle is stationary. 10. The combination, with an enclosed space, and air conditioning apparatus to cool said space, of a hydraulic motor for driving said apparatus, a heating unit arranged within said space and provided with a restricted passageway to cause liquid forced therethrough to have heat generated therein to heat said space, a pump, means for directing liquid from said pump to said motor and to said unit selectively, a variable speed drive for driving said pump, and fluid actuated means responsive to variations in the velocity of liquid circulated by said pump for varyin pump displacement to thereby maintain pump output substantially constant within a wide range of driving speeds. l

11. The combination, with an enclosed space, of a heating unit having a restricted passageway to cause liquid forced therethrough to generate heat in said unit to heat said space a variable displacement pump for supplying liquid to said unit. means for driving said pump at varying speeds, and means responsive to variations in the velocity of the liquid delivered by said pump for varying pump displacement to thereby maintain hydraulic motor for driving said apparat a variable speed source of power, of a variable the volumetric delivery of said pump approximately constant.

'12. The combination, with an enclosed space,

refrigerating apparatus for cooling said space, a. hydraulic motor for driving said apparatus, and a variable speed source of power, of a variable displacement pump for supplying motive liquid to said motor connected to said source to be driven at varying speeds therefrom, said pump having a displacement varying member constant- 1y urged toward zero displacement, position, a hydraulic servo-motor for moving said member toward mmdmumdisplacement position, means for supplying motive liquid to said servo-motor to operate the same, and fluid actuated means responsive to variations in the velocity of the liquid discharged by said pump for controlling the flow of liquid to and from said servo -motor to thereby cause pump displacement to be varied inversely to variations in pump speed.

13. The combination, with an enclosed space, refrigerating apparatus for cooling said space, a and displacement pump for supplying motive liquid to said motor connected to said source to be driven at varying speeds therefrom, said pump having a displacement varying member constantly urged toward zero displacement position, a hydraulic servo-motor for moving said member toward maximum displacement position, a constant displacement pump driven in unison with said variable pump for supplying motive liquidto said servo-motor to operate the same, and fluid actuated means responsive to variations in the velocity of the liquid discharged by said variable from said servo-motor to thereby cause pump displacement to be varied inversely to variations in pump speed.-

pump for controlling the flow of liquid to and 14. The combination, with an enclosed space.

refrigerating apparatus for cooling said space, a hydraulic motor for driving said apparatus, and a variable speed source of power, of a variable displacement pump for supplying motive liquid to said motor connected to said source to be driven at varying speeds therefrom, said pump having a displacement varying member constantly urged toward zero displacement position, a hydraulic servo-motor for moving said member toward maximum displacement position, a source of control liquid, and means for directing control liquid from saidsource to said servo-motor to operatethe same and including a valve operable in response to variations in the velocity of the liquid discharged by said pump for controlling the flow of control liquid to and from said servo-motor to thereby enable said servo-motor to move said member in a direction to increase pump displacement as pump speed decreases and to permit said member to move in a direction to decrease pump displacement as pump speed increases.

15. The combination, with a vehicle, apparatus carried by said vehicle and a hydraulic motor for.

driving'said apparatus, of a variable displacement pump for supplying motive liquid to said motor, said pump being driven at varying speeds by motion imparted thereto from said vehicle and having a displacement varying member constantly urged toward zero displacement position, a hydraulic servo-motor for moving said member toward maximum displacement position, a constant displacement pump driven in unison with said variable pump for supplying liquid to said'servomotor to operate the same, and meansfor directing liquid from said constant displacement pump to said servo-motor and including a valve operabe in response to variations in the velocity of the liquid discharged by said variable pump for controlling the flow of liquid to and from said servomotor to thereby enable said servo-motor to move said pump being driven at varying speeds by motion imparted thereto from said vehicle and having a displacement varying member constantly urged toward zero displacement position,

a hydraulic servo-motor for moving said member toward maximum displacement position, a source of control liquid, means for directing control liquid from its source to said servo-motor to operate the same and including a valve operable in response to variations in the velocity of the liquid discharged by said pump for controlling the flow of control liquid to and from said servo-motor to thereby enable said servo-motor to move said member in a direction to increase pump displacement as pump speed decreases and to permit said member to move in a direction to decrease pump displacement as pump speed increases, spring means for shifting said valve to a position to permit said member to move in a direction to decrease pump displacement, and means operable by liquid supplied from said source for preventing said spring means from afiecting the operation of said valve.

17. The combination, with a vehicle, apparatus carried by said vehicle and 'a hydraulic motor for" of the liquid discharged by said variable pump conditioning apparatus for controlling the flow of liquid to and from said servo-motor to thereby enable said servo-motor to move said member in a direction to increase pump displacement as pump speed decreases and to permit said member to move in a direction to decrease pump displacement as pump speed increases, spring means for shifting said valve to a position to permit said member to move in a direction to decrease pump displacement, and means operableby liquid supplied by said constant displacement pump for preventing said spring means from affecting the operation oi said valve.

18. The combination, with a vehicle having air of a main hydraulic motor for driving sa' .ratus, a variable displacement pump 2 supplying liquid to said motor to drive thesame, means for driving said pump from a turnable part of said vehicle. fluid actuated means responsive to variations in the velocity oi the liquid delivered by said pump for varying pump displacement inversely to variations in pump speed, a gear pump driven in unison with said variable pump for supplying motive liquid to said fluid actuated means, an auxiliary hydraulic motor connected in series with said main motor, and means responsive to variations inthe velocity of the liquid discharged from said auxiliary motor for by-passing around said auxiliary motor a part of the liquid discharged from said main motor to thereby govern the speed oisaid auxiliary motor independently of the speed oi said main motor.

19. The combination, with a vehicle having air conditioning apparatus of a main hydraulic motor for driving said apparatus, a variable displacement pump ior supplyingiiliquid to said motor to drive the same, means fongdriving said pump from a turnable part of said hicle, iiuid actuated means responsive to variati' the velocity of the liquid delivered by said pump for varying pump displacement inversely to variations in pump speed, a gear pump driven in unison with said variable pump for supplying motive liquid to said fluid actuated means, an auxiliary hydraulic motor connected in series with said main motor, means responsive to variations in the velocity of the liquid discharged from said auxiliary motor for bypassing around said auxiliary motor a part of the liquid discharged from said main motor to thereby govern the speed 0! said auxiliary motor independently of the speed 01' said main motor, and an electric motor connected to said main motor and adapted to be connected into a stationary electric circuit when said vehicle is stationary to drive said main motor and cause it to function as a pump and deliver liquid for driving said auxiliary motor.

20-. The combination, with a vehicle having air conditioning apparatus, of a main hydraulic motor for driving said apparatus, a variable displacement pump for supplying liquid to said motor to drive the same, means for driving said pump from a turnable part of said vehicle, fluid actuated means responsive to variations in the velocity of the liquid delivered by said pump for varying pump displacement inversely to variations in pump speed, a gear pump driven in unison with said variable pump for supplying motive liquid to said fluid actuated means, an auxiliary hydraulic motor connected in series with said main motor, means responsive to variations in the velocity of the liquid discharged from said auxiliary motor for bypassing around said auxiliary motor a part of the liquid discharged from said main motor to thereby govern the speed of said auxiliary motor independently oi the speed of said main motor, an electric motor connected to said main motor and adapted to be connected into a stationary electric circuit when said vehicle is stationary to drive said main motor and cause it to function as a pump and deliver liquid for driving said auxiliary motor, and a gear pump driven in unison with said main motor for maintaining pressure at the intake oi said main motor and in said bypassing means.

21. The combination, with a vehicle and air conditioning apparatus to cool the interior of said vehicle, of a hydraulic motor for driving said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means for directing liquid from said pump to said motor and to said radiator selectively including a hydraulically operated selector valve, a pilot valve for controlling operation of said selector valve,

and means responsive to variations in the temperature within said vehiclefor operating said pilot valve.

' 22. The combination, with a vehicle and air.

conditioning apparatus to cool the interior of said vehicle, of a hydraulic motor for driving said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means 'for directing liquid from said pump to said motor and to said radiator selectively including a hydraulically operated selector valve, a control valve for controlling operation of said motor, a pilot valve for controlling operation of each of said valves, and means responsive to variations in the temperature within said vehicle for operating each of said pilot valves.

23. The combination, with a vehicle and air .conditioning apparatus to cool the interior of said vehicle, of a hydraulic motor for drivin said apparatus, a radiator arranged within said vehicle to cause liquid forced therethrough to heat the interior of said vehicle, a pump driven by motion imparted thereto from said vehicle, means for directing liquid from said pump tosaid motor and to said radiator selectively including a hydraulically operated selector valve, 9. control valve connected in series with said selector valve for controlling operation of said motor, a pilot valve for controlling operation of each of said valves, and means responsive to variations in the temperature within said vehicle for operating each of said pilot valves.

24. The combination, with a vehicle having apparatus for cooling the interior thereof, of a hydraulic motor for driving said apparatus, a pump for supplying motive liquid to said motor driven by motion imparted thereto from said vehicle, an auxiliary pump driven by motion imparted thereto from said vehicle, a hydraulically operated valve for controlling the delivery of liquid from. said variable pump to said motor, yieldable means constantly urging said valve toward a position to bypass said motor, and means for directing liquid from said auxiliary pump to said valve to move it to a position to direct liquid to said motor.

25. The combination, with a vehicle having apparatus for cooling the interior thereof, of a hydraulic motor for driving said apparatus, a variable displacement pump for supplying motive liquid to said motor driven by motion imparted thereto from said vehicle, said pump having a; displacement varying member constantly urged toward zero displacement position, an auxiliary for moving said displacement varying member toward maximum displacement position, means responsive to variations in the velocity of the liquid discharged by said variable pump for controlling the delivery of liquid to said servo-motor to thereby control pump delivery, a hydraulically operated valve for controlling the delivery of liquid from said variable pump to said motor, yieldable means constantly urging said valve toward a position to bypass said motor, and means for directing liquid from said auxiliary pump to said valve to move it to a position to direct liquid to said motor.

26. The combination, with a vehicle having apparatus for cooling the interior thereof, of a hydraulic motor for driving said apparatus, a pump for supplying motive liquid to said motor driven by motion imparted thereto from said vehicle, an auxiliary pump driven by motion imparted thereto from said vehicle, a hydraulically operated valve for controlling the delivery of liquid from said variable pump to said motor, yieldable means constantly urging said valve toward a position to bypass said motor, means for directing liquid from said auxiliary pump to said valve to move it to a position to direct liquid to said motor, a pilot valve for controlling the delivery of liquid from said auxiliary pump to said valve, and means responsive to variations in the temperature within said vehicle for operating said pilot valve.

2'7. The combination, with a vehicle having apparatus for cooling the interior thereof, of a hydraulic motor for driving said apparatus, a variable displacement pump for supplying motive liquid to said motor driven by motion imparted thereto from said vehicle, said pump having a displacement varying member constantly urged toward zero displacement position, an auxiliary pump driven by motion imparted thereto from said vehicle. a hydraulic servo-motor operated by liquid supplied thereto from said auxiliary pump for moving said displacementi' varying member toward maximum displacement position, means responsive to variations in the velocity of the liquid discharged by said variable pump for con-- trolling the delivery of liquid to said servo-motor to thereby control pump delivery, a hydraulically operated valve tor controlling the delivery oi liquid from said variable pump to said motor, yieldable means constantly urging said valve toward a position to bypass said motor, means for directing liquid from said auxiliary pump to said valve to move it to a position to direct liquid to said motor, a pilot valve for controlling the delivery of liquid from said auxiliary pump to said valve, and means responsive to'varlations in the temperature within said vehicle for operatin said pilot valve.

WALTER FERRIS. JAMES K. DOUGLAS. GEORGE H. FOBIAN. 

